US4790700A - Integral spring flexure for use with high speed rotating shafts - Google Patents

Integral spring flexure for use with high speed rotating shafts Download PDF

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Publication number
US4790700A
US4790700A US06/940,948 US94094886A US4790700A US 4790700 A US4790700 A US 4790700A US 94094886 A US94094886 A US 94094886A US 4790700 A US4790700 A US 4790700A
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United States
Prior art keywords
slots
spring
lands
integral
land
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Expired - Lifetime
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US06/940,948
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English (en)
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Everett H. Schwartzman
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Individual
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Individual
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Priority claimed from US06/635,716 external-priority patent/US4640653A/en
Application filed by Individual filed Critical Individual
Priority to US06/940,948 priority Critical patent/US4790700A/en
Priority to DE8787310914T priority patent/DE3769101D1/de
Priority to EP87310914A priority patent/EP0271355B1/de
Priority to JP62315068A priority patent/JPS6455442A/ja
Priority to US07/234,590 priority patent/US4913605A/en
Application granted granted Critical
Publication of US4790700A publication Critical patent/US4790700A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/72—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members with axially-spaced attachments to the coupling parts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B31/00—Chucks; Expansion mandrels; Adaptations thereof for remote control
    • B23B31/02—Chucks
    • B23B31/10—Chucks characterised by the retaining or gripping devices or their immediate operating means
    • B23B31/12—Chucks with simultaneously-acting jaws, whether or not also individually adjustable
    • B23B31/20—Longitudinally-split sleeves, e.g. collet chucks
    • B23B31/201—Characterized by features relating primarily to remote control of the gripping means
    • B23B31/207—Characterized by features relating primarily to remote control of the gripping means using mechanical transmission through the spindle
    • B23B31/2073—Axially fixed cam, moving jaws
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23B—TURNING; BORING
    • B23B31/00—Chucks; Expansion mandrels; Adaptations thereof for remote control
    • B23B31/02—Chucks
    • B23B31/24—Chucks characterised by features relating primarily to remote control of the gripping means
    • B23B31/26—Chucks characterised by features relating primarily to remote control of the gripping means using mechanical transmission through the working-spindle
    • B23B31/261—Chucks characterised by features relating primarily to remote control of the gripping means using mechanical transmission through the working-spindle clamping the end of the toolholder shank
    • B23B31/266—Chucks characterised by features relating primarily to remote control of the gripping means using mechanical transmission through the working-spindle clamping the end of the toolholder shank using a threaded spindle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F1/00—Springs
    • F16F1/02—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant
    • F16F1/025—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant characterised by having a particular shape
    • F16F1/028—Springs made of steel or other material having low internal friction; Wound, torsion, leaf, cup, ring or the like springs, the material of the spring not being relevant characterised by having a particular shape cylindrical, with radial openings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T409/00—Gear cutting, milling, or planing
    • Y10T409/30—Milling
    • Y10T409/309352—Cutter spindle or spindle support
    • Y10T409/309408—Cutter spindle or spindle support with cutter holder
    • Y10T409/309464—Cutter spindle or spindle support with cutter holder and draw bar

Definitions

  • the present invention relates to an integral one piece spring and more particularly to an improved integral one-piece spring especially adapted for use at relatively high rotational speeds, for example, for use in a relatively high speed spindle having an accurate axis of rotation.
  • Flexures are used to connect two members of a system between which a relatively small movement is required. This method of construction has a great advantage of simplicity, coupled with complete freedom from friction and backlash, which are very detrimental to the performance of said system.
  • the spring structure of the previously filed application above identified operates in a manner which is quite acceptable.
  • the improved structure of this invention constitutes an improvement in the structure previously described and is believed to represent an improvement generally in the structure of integral machined one-piece springs.
  • the improvements of this invention relate to a structure in which the stresses are more evenly distributed so as to assure essentially an even stress distribution in the spring structure.
  • this structure involves modification of the slot widths in selected regions of the spring and providing controlled radial dimensions of the lands so that the spring is not subject to high localized and uneven stresses which tend to promote failure at certain regions of the spring. The result is a much improved machined spring structure having use in a much wider field than merely relatively high speed spindles.
  • FIG. 1 is a cross-sectional drawing showing the structural relationships of the major components in accordance with the principles of the present invention
  • FIG. 2 is an illustrative view showing the construction of said integral spring
  • FIG. 2a is a view in perspective of an integral spring in accordance with the present invention in which the slots are radiused;
  • FIG. 2b is an illustrative view showing the spring nut in relationship to the drawbar and collet assembly
  • FIG. 2c is a view in perspective of a form of integral spring in accordance with this invention.
  • FIG. 3 is a cross-sectional view showing the design and construction of an alternate method of design of said integral spring
  • FIG. 3B shows the view A--A of FIG. 3
  • FIG. 4 is a view in perspective of another form of integral spring in accordance with the present invention.
  • FIG. 5 is an enlarged fragmentary view of a portion of the integral spring of FIG. 4;
  • FIG. 5a is a plan view, for purposes of illustration, of an integral spring in accordance with this invention.
  • FIG. 6 is a diagrammatic view illustrating the stress distribution over the solid beam portion of the integral spring
  • FIG. 7 is a plan view of the underside of an integral spring of the present invention illustrating one of the features previously illustrated diagrammatically in FIG. 6;
  • FIG. 8 is a view in perspective of a spring in accordance with this invention for use in a high speed spindle.
  • FIG. 9 is a view partly in section and partly in elevation of an improved spindle in accordance with this invention in which a non-rotating actuating rod is used.
  • a major advantage of this spindle design is that all of the individual parts return to their respective positions with a minimum of deviation after each actuation, so as to prevent or minimize the occurrence of out-of-balance forces.
  • the type of spring best suited for this application is one that is of the integral machine type as shown in FIG. 2.
  • This type of spring can not only be designed to have the desired or required spring characteristics, but is also a true flexure integral with the assembly. It therefore minimizes any geometric change, and prevents out-of-balance forces due to the shifting of the part's position.
  • FIG. 1 shows such a spindle design in which the shaft 3 is hollow so as to allow for the use of a drawbar 5.
  • Said drawbar 5 is attached to collet 7 by means of threads 9.
  • Collet 7 is contracted around tool 11 by means of its tapered surface 13 and corresponding tapered surface in shaft 3.
  • Drawbar 5 is kept in tension by integral machine type spring 17 located at the opposite end of shaft 3.
  • Spring 17 is constrained by shaft 3 at point 15 on one end, and head 21 of drawbar 5 at its other end.
  • Drawbar 5 is actuated by force applied to its head 21, which is supplied by any means, located at point 23, such a pneumatic, hydraulic, magnetic, or electrical/electro-mechanical.
  • Shaft 3 is maintained in a true concentric position relative to housing 19 by a bearing system 25.
  • Shaft 3 is powered by any desired means 27, such as an electric motor, pneumatic motor, hydraulic motor, or various types of turbines.
  • the spring rotates with the shaft 3 and may be attached at 15 by keys, splines, screw threads, or by virtue of the spring biased engagement between the spring and the shaft.
  • a drawbar system is utilized to actuate the collet or chuck.
  • An integral spring nut assembly is used to close the chuck and maintain the required force to hold the tool bit in the collet or chuck.
  • the spring nut is machined with slots to generate the required geometry for creating the spring and is made in one piece.
  • the one piece construction minimizes moving parts and eliminates the movement of any of the rotating parts relative to each other. This feature assures that no out-of-balance condition, nor shifting of the true mass axis with the geometric axis will occur during operation. This feature maintains the best concentricity and insures a minimum of vibration during operation.
  • FIGS. 2, 2a, 2b and 2c show that the construction of the integral spring nut 17 is obtained by machining alternate layers of slots 29 partially through a tubular cross section 31.
  • the solid interconnecting section 33 of each alternate layer are disposed an equal number of degrees apart, for example, 90 degrees apart so as to maintain the integrity of said spring.
  • the thickness of each spring member 35 and wall thickness of the tubular cross section 31 determine the stiffness and stress level of each spring member or lands 35.
  • the number of slots 29 or number of spring members 35 in conjunction with the thickness and diameter of the tubular cross section determine the spring stiffness. The desired spring characteristics can thus be obtained to hold collet 7 around tool 11 within shaft 3 by the force applied by said spring nut 17.
  • FIG. 3 shows an alternate integral spring nut design which is comprised of metal diaphragms 39. Said diaphragm's thickness 41 and diameter 43 determine the stress levels and force load characteristics. The number of said diaphragms 39 also determines the overall spring stiffness. Each diaphragm can be separately manufactured and joined by welding, brazing, or any other suitable means at their respective outer circumference 47 and inner circumference 49.
  • FIG. 3B shows another alternative to the design of the type of integral spring nut as described in FIG. 3.
  • notches 51 are utilized to decrease the spring stiffness and minimize stress in said diaphragms 39.
  • the inner circumference 49 is still completely welds or joined as described in FIG. 3.
  • the outer circumference 47 is now only joined with each alternate diaphragm between each notch as shown.
  • an improved form of integral spring 60 is illustrated as being hollow and generally cylindrical in shape and including spaced end faces 62 and 63.
  • the wall 65 of the spring between the end faces 62 and 63 includes a plurality of tiered slots 66 and tiered lands 68, the slots and lands extending circumferentially, as shown.
  • the number of tiers may vary depending upon the strength and length and other characteristics desired in the spring while the circumferential dimension of each of the slots and lands may vary, again depending on the characteristics desired in the spring.
  • each slot tier includes two slots 71 and 72 and two circumferentially spaced solid sections 73 and 74 between the slots.
  • each slot tier includes two slots 71 and 72 and two circumferentially spaced solid sections 73 and 74 between the slots.
  • the junction between the slot and the associated solid section is radiused as indicated at 75 to reduce stress and to minimize fatigue at the junction of the solid section and the slot.
  • the land tier 68 includes a plurality of circumferentially extending lands 76 located between the axially spaced slots.
  • the circumferential land 76 is one-half the circumferential dimension of the slot, i.e., there are twice as many lands in a tier as there are slots.
  • each tier is opposite to each other while the cooperating lands of each tier are also opposite to each other as illustrated.
  • there is a slot opposite a land but the slots and lands are disposed at 120 degrees to each other.
  • the respective tiers are arranged such that as one traces axially of the spring, there is a slot, with a land below it and a slot below the land, or there may be a land, with a slot below it with a land below the slot.
  • the use of two slots and two solid sections provides four lands in each of the respective land tiers resulting in the formation of four lobes 80, 81, 82, and 83 disposed at 90 degrees with respect to each other.
  • lobes 81 and 83 are formed by the solid sections of one slot tier
  • lobes 80 and 82 are formed by the solid section of another tier, above or below the one tier.
  • the number of lobes depends upon the number of slots and the solid sections in each slot tier.
  • the number of lobes is related to the number of solid sections in each tier and the number of solid sections is directly related to the number of slots, which may vary in accordance with the limits herein described.
  • the end faces 62 and 63 are fixed during flexure in that they are in contact with a support surface or element. Thus, the end faces do not move because they are fixed. Since the end faces are fixed, this has an effect on the regions of the spring which are subject to possible fatigue failure. More specifically, the land on each side of a slot each tends to move one half of the axial width of the slot. If the slot associated with the end faces were a full width, then the top and bottom lands would tend to move more than one half the slot width thus tending to induce premature fatigue in the top and bottom lands.
  • the axial width of the slot at the top and bottom is one half of the axial width of the slots between the top and bottom as seen in FIG. 5.
  • the top slot 85 and the bottom slot 88 are each of a predetermined dimension which is less than the predetermined axial width dimension of the slots therebetween, and preferably one half the axial width of the slots 90, 91 which are between the end slots. In this way, it is assured that the top and bottom lands cannot move more than a distance amounting to about one half of the normal slot width.
  • the slot associated with the top and bottom lands were of the same predetermined axial width dimension as the remaining slots.
  • data collected through testing indicated that the top and bottom lands were capable of moving axially more than one half the axial slot width, while the lands between the end lands were capable of moving about one half of the slot width.
  • top and bottom lands were moving axially more than half the slot width and the lands between the end lands were moving a maximum of one half the slot width, the end lands were being stressed greater than the lands between the end lands.
  • Actual experimental performance data confirmed that after prolonged cycling one of the top or bottom or both lands tended to fail due to greater stresses as compared to the lands between the end lands.
  • the stresses may be more evenly distributed across all of the lands of the spring in an integral machined spring if the slots adjacent to and immediately below or above the end lands are dimensioned such that their predetermined axial width is less than the predetermined axial width of the remaining slots between the end lands.
  • the end slots each are of a predetermined axial width which is less than the predetermined axial width of the slots between the end-most slots, and preferably one half the axial width dimension of the remaining slots. In this way, the end lands cannot move more than one half the slot width since the slot associated with the top and bottom lands is one half the width as compared to the remaining slots.
  • a land 100 is shown as a solid beam between adjacent slots.
  • the center section 102 is least stressed as compared to the end sections 103 and 104.
  • the lands are uniquely configured.
  • the lobes are thicker in radial cross section at the region where the lands join the body than in the region between the lobes.
  • a four lobe configuration is shown including lobes 105, 106, 107, and 108, each having a radial dimension to the outer surface 110 which is greater than that of the pockets 111, 112, 113 and 114 between the lobes.
  • the adjacent pairs of lobes, e.g., 105-106 represent the ends of a land 103 and 104, while the pocket 114 represents the mid-region 102 of a land 100.
  • each land in radial dimension, is configured such that the ends 103 and 104 are of a maximum radial dimension while the center 102 is of a lesser radial dimension.
  • the portion between the center and each end of each land represents a transition zone in which the radial dimension changes from a maximum to a minimum dimension.
  • the portion of the lands which is stressed more is thicker in radial dimension than the portion of the land which is least stressed. The result is that the stresses are uniformly distributed by having the more stressed areas thicker radially than the least stressed intermediate regions.
  • the same construction may be used in other than four lobe systems. It is also apparent that the dimensions may be calculated from spring calculations to provide a spring of a predetermined spring characteristic, as is well known in the art. It is also apparent that the fabrication of the spring is relatively simple. More specifically, the slots are cut to provide the slots and lands, the top and bottom slots preferably being one half the axial dimension of the slots between the end slots. Thereafter the pockets are formed, as for example drilling or otherwise machining the pockets at the regions of the cylinder which form the ends of the lands.
  • lobes and pockets are illustrated as generally circular is section, this is done for symmetry and symmetrical stress distribution and is the preferred form. It will be apparent that other forms may be used depending upon the stress condition and the use of the spring. It is also apparent that the lobes may be formed on the outer surface rather than the inner surface as illustrated in the representative drawing.
  • FIG. 8 illustrates a spring 120 as described with respect to FIGS. 4-7 in which an integral nut 125 is provided on one end 127 of the spring.
  • This particular structure may be used in a spindle as already described, or in other forms of spindle assemblies.
  • FIG. 9 illustrates a high speed spindle assembly in which a shaft 130 in the form of rotor is hollow through the center to allow the use of a non-rotating actuator rod or push bar 133 located in the center aperture of the rotor.
  • a machined spring 135 Located to the front of the front end ofthe push bar 133 and arranged concentrically therewith is an integral machined spring 135 which may be any of the machined springs already described.
  • the machined spring 135 maintains a collet 137 in contact with the shaft 130.
  • the collet 137 may be screwed or otherwise fixed to the machined spring 135.
  • the collet is contracted around a tool, indicated at 139 by the tapered surfaces 141 in the collet holder 143 which is non-rotating relative to the shaft 130 and affixed thereto by screws 145 although one may use other affixing means.
  • the tool 139, the collet 137 and the collet holder 143 rotate with the shaft 130.
  • the non-rotating bar 133 may be actuated axially through the shaft 130 by any one of several different means such as a magnetic force, or pnuematic force or the like to actuate the collet for a change of tools.
  • the tool is secured in the collet by the spring force of the machined spring 135 since the push bar 133 is normally biased away from the machined spring by a spring mechanism 147 which urges the push bar away from the machined spring, as shown.
  • the push bar is urged towards the machined spring to urge the collet axially to release the tool and spring biased by the machined spring into the tool lock position.
  • the shaft 130 is mounted in a true concentric position relative to a housing 151 by a bearing assembly schematically illustrated at 153.
  • the bearing assembly also includes a bearing mechanism along the lateral face of the shaft, also indicated at 153.
  • the shaft may be rotated by any desired means 155, which in the form illustrated may be an electric motor having the armature on the shaft and the stator 155 supported by the housing. It is understood that the motor may be a pneumatic motor or a hydraulic motor or any one of several different types of turbines. Since the machined spring is mounted on the shaft 130 as indicated at 157 through the use of pins 159 or the like, it rotates with the shaft.
  • the actuating or push rod 133 is non rotating but is axially moveable relative to the housing and is used to actuate the collet when the shaft 130 is not rotating in order to effect a tool change.
  • the use of an integral spring nut operates to keep the collet closed to maintain the tool in the collet. Since the collet, tool and integral spring nut rotate at relatively high speeds, the advantages already described are obtained.
  • the use of a one-piece integral machined spring minimizes moving parts and eliminates the movement of the rotating parts relative to each other, especially radial movements. This structure assures no out-of-balance conditions, and assures that there is not shifting of the true mass with respect to the geometric axis during high speed rotation.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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US06/940,948 1984-07-30 1986-12-12 Integral spring flexure for use with high speed rotating shafts Expired - Lifetime US4790700A (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US06/940,948 US4790700A (en) 1984-07-30 1986-12-12 Integral spring flexure for use with high speed rotating shafts
DE8787310914T DE3769101D1 (de) 1986-12-12 1987-12-11 Flexibeles federelement zur verwendung bei hochgeschwindigkeitswellen.
EP87310914A EP0271355B1 (de) 1986-12-12 1987-12-11 Flexibeles Federelement zur Verwendung bei Hochgeschwindigkeitswellen
JP62315068A JPS6455442A (en) 1986-12-12 1987-12-12 Integral type machining spring assembly
US07/234,590 US4913605A (en) 1984-07-30 1988-08-22 Integral spring flexure for use with high speed rotating shafts

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/635,716 US4640653A (en) 1984-07-30 1984-07-30 Integral spring flexure for use with high speed rotating shafts
US06/940,948 US4790700A (en) 1984-07-30 1986-12-12 Integral spring flexure for use with high speed rotating shafts

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
US06/635,716 Continuation-In-Part US4640653A (en) 1984-07-30 1984-07-30 Integral spring flexure for use with high speed rotating shafts

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US07/234,590 Division US4913605A (en) 1984-07-30 1988-08-22 Integral spring flexure for use with high speed rotating shafts

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US4790700A true US4790700A (en) 1988-12-13

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US06/940,948 Expired - Lifetime US4790700A (en) 1984-07-30 1986-12-12 Integral spring flexure for use with high speed rotating shafts

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US (1) US4790700A (de)
EP (1) EP0271355B1 (de)
JP (1) JPS6455442A (de)
DE (1) DE3769101D1 (de)

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US4913605A (en) * 1984-07-30 1990-04-03 Schwartzman Everett H Integral spring flexure for use with high speed rotating shafts
US5078558A (en) * 1990-02-16 1992-01-07 Hitachi Seiko, Ltd. Low mass spindle and Z-axis unit
US5500122A (en) * 1994-05-11 1996-03-19 Uop Stacked fluid-separation membrane disk module assemblies
US5520807A (en) * 1994-05-11 1996-05-28 Uop Stacked fluid-separation membrane disk module assemblies
US5536405A (en) * 1994-05-11 1996-07-16 Uop Stacked membrane disk assemblies for fluid separations
US6337142B2 (en) 1997-07-02 2002-01-08 Stryker Trauma Gmbh Elongate element for transmitting forces
US6929437B1 (en) * 2002-02-22 2005-08-16 Ballado Investments, Inc. Spindle with axially acting collet-opening device
US20070057473A1 (en) * 2003-05-22 2007-03-15 Pavey Christopher J Rotary tool holder assemblie
WO2008015455A1 (en) * 2006-08-03 2008-02-07 Gsi Group Limited Rotary tool holder assemblies
WO2008015454A1 (en) * 2006-08-03 2008-02-07 Gsi Group Limited Tool holder assemblies
GB2453701A (en) * 2006-08-03 2009-04-15 Gsi Group Ltd Tool holder assemblies
US20090321668A1 (en) * 2008-06-27 2009-12-31 Caterpillar Inc. Distributed stiffness biasing spring for actuator system and fuel injector using same
US8826547B2 (en) 2008-11-25 2014-09-09 Robert Bosch Gmbh Impact absorption drive mechanism for a reciprocating tool
US9303664B2 (en) 2011-12-06 2016-04-05 Nancy K. Keech Quick lock fastener
US20170129019A1 (en) * 2015-11-06 2017-05-11 Ott-Jakob Spanntechnik Gmbh Clamping device
US10933525B2 (en) * 2018-07-04 2021-03-02 Fanuc Corporation Horizontal articulated robot
US20210288425A1 (en) * 2018-11-30 2021-09-16 Corning Optical Communications Rf Llc Compressible electrical contacts with divericated-cut sections
US20220074459A1 (en) * 2020-09-07 2022-03-10 Honda Motor Co., Ltd. Resinous spring
US11408478B2 (en) * 2016-06-17 2022-08-09 Scuola Superiore Di Studi Universitari E Di Perfezionamento Sant'anna Joint for transmitting a torsional load with elastic response
US11781579B1 (en) * 2019-05-28 2023-10-10 Allfasteners USA, LLC Blind bolt with collapsible shear sleeve assembly
US12176638B2 (en) 2019-11-30 2024-12-24 Corning Optical Communications RF, LLC Connector assemblies
US12212083B2 (en) 2020-11-30 2025-01-28 Corning Optical Communications Rf Llc Compressible electrical assemblies with divaricated-cut sections
RU238151U1 (ru) * 2025-07-04 2025-10-17 Общество с ограниченной ответственностью "НПП Куйбышев Телеком-Метрология" Пружина ультразвукового приёмопередатчика

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FR2827649B1 (fr) 2001-07-17 2003-12-26 Somfy Dispositif monobloc deformable de transmission d'un couple
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EP2947342B1 (de) 2014-05-19 2017-04-05 Goodrich Actuation Systems Ltd. Drehmomentbegrenzer
IT201600107750A1 (it) * 2016-10-26 2018-04-26 Essetre S R L Elettromandrino per cambio-utensili automatico e centro di lavoro con dispositivo di cambio-utensili automatico
US11033971B2 (en) * 2017-05-09 2021-06-15 Schaublin Sa Clamping device for holding a collet
US12480558B2 (en) * 2021-08-10 2025-11-25 Raytheon Company 3-axis tunable metal isolator
CN115182937B (zh) * 2022-07-18 2023-06-02 西南石油大学 一种用于曲轴振动控制的变刚度叠片联轴器

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US7950596B2 (en) 2008-06-27 2011-05-31 Caterpillar Inc. Distributed stiffness biasing spring for actuator system and fuel injector using same
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US9931700B2 (en) * 2015-11-06 2018-04-03 Ott-Jakob Spanntechnik Gmbh Clamping device
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US11725707B2 (en) 2016-06-17 2023-08-15 Scuola Superiore Di Studi Universitari E Di Perfezionamento Sant'anna Joint for transmitting a torsional load with elastic response
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US12482972B2 (en) * 2018-11-30 2025-11-25 Corning Optical Communications Rf Llc Compressible electrical contacts with divericated-cut sections
US11781579B1 (en) * 2019-05-28 2023-10-10 Allfasteners USA, LLC Blind bolt with collapsible shear sleeve assembly
US12176638B2 (en) 2019-11-30 2024-12-24 Corning Optical Communications RF, LLC Connector assemblies
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US12212083B2 (en) 2020-11-30 2025-01-28 Corning Optical Communications Rf Llc Compressible electrical assemblies with divaricated-cut sections
RU238151U1 (ru) * 2025-07-04 2025-10-17 Общество с ограниченной ответственностью "НПП Куйбышев Телеком-Метрология" Пружина ультразвукового приёмопередатчика

Also Published As

Publication number Publication date
JPS6455442A (en) 1989-03-02
DE3769101D1 (de) 1991-05-08
EP0271355A3 (en) 1989-02-22
EP0271355A2 (de) 1988-06-15
EP0271355B1 (de) 1991-04-03

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